CN103154568A - 9-speed planetary-gear automatic transmission - Google Patents

9-speed planetary-gear automatic transmission Download PDF

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Publication number
CN103154568A
CN103154568A CN2011800453311A CN201180045331A CN103154568A CN 103154568 A CN103154568 A CN 103154568A CN 2011800453311 A CN2011800453311 A CN 2011800453311A CN 201180045331 A CN201180045331 A CN 201180045331A CN 103154568 A CN103154568 A CN 103154568A
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CN
China
Prior art keywords
gear
automatic transmission
planetary
planetary gear
clutch
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN2011800453311A
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Chinese (zh)
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CN103154568B (en
Inventor
U·奥内穆斯
T·马沙尔
A·马丁
L·沃尔夫
A·森夫特
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of CN103154568A publication Critical patent/CN103154568A/en
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Publication of CN103154568B publication Critical patent/CN103154568B/en
Expired - Fee Related legal-status Critical Current
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention relates to a 9-speed planetary-gear automatic transmission, in particular a planetary-gear automatic transmission having nine forward gears, wherein precisely one gearbox input element (GE), precisely one gearbox output element (GA), precisely four planetary gear sets (PGS1-PGS4) and precisely six shifting devices (B03, B06, K14, K18, K38, K78) are provided for selecting the individual gears of the planetary-gear automatic transmission.

Description

9 gear planetary gear automatic transmissions
The present invention relates to a kind of planetary gear automatic transmission of feature as claimed in claim 1.
The objective of the invention is, a kind of planetary gear automatic transmission is provided, this planetary gear automatic transmission has more forward gear than the 8 gear-automatic transmission that existed on current market and has simple as far as possible project organization.
This purpose is achieved by the feature of claim 1.The design that the present invention is favourable and further formation are drawn by dependent claims.
Basic principle of the present invention is a kind of like this planetary gear automatic transmission, the planetary gear automatic transmission that particularly has nine forward gears, wherein, this planetary gear automatic transmission has just in time four planetary gear set and six shifting elements that arrange for each gear that switches planetary gear automatic transmission just in time.
These shifting elements several or can be all the shifting element that friction is sealed or shape is sealed, for example multidisc clutch or multi-plate brake or jaw clutch.
If be provided with the sealed shifting element of one or more shape, can configure respectively a synchronizer for indivedual or each shifting element in the sealed shifting element of these shapes.
Described planetary gear automatic transmission has speed changer input end and speed changer output terminal, and described speed changer input end for example consists of by transmission input shaft, and described speed changer output terminal can consist of by transmission output shaft." startup module " can be prepended to planetary gear automatic transmission, this startup module for example can consist of by the torque converter (fluid torque converter) of fluid power.Therefore the speed changer input end can be connected with " driven end " of the torque converter of fluid power.
The speed changer output terminal can be coupled with the Power Train of Motor Vehicle.In the situation of all-wheel powered vehicle, the speed changer output terminal for example can be connected with the input end of full wheel transfer case (Allradverteilergetriebe).
Hereinafter further set forth the present invention in connection with accompanying drawing.In accompanying drawing:
Fig. 1 is the embodiment of planetary gear automatic transmission of the present invention;
Fig. 2 is for being used for the chart at explanation transmission gear ratio interval, and this transmission gear ratio interval can utilize the speed changer shown in Fig. 1 to realize; With
Fig. 3 is the gearshift array, and is closed in order to explanation which shifting element in each gear of determining.
Planetary gear automatic transmission shown in Figure 1 has transmission input shaft GE and transmission output shaft GA.
In addition, be provided with just in time four planetary gear set, particularly, the direction from speed changer input end GE towards speed changer output terminal GA is observed the first planetary gear set PGS1, the second planetary gear set PGS2, third planet gear train PGS3 and fourth planet gear train PGS4.
In addition, be provided with just in time six shifting elements for each gear that switches to planetary gear automatic transmission, i.e. first clutch K78, second clutch K18, three-clutch K14, four clutches K38, the first break B06 and second brake B03.
The first planetary gear set PGS1 have the first sun gear P1S that first an internal gear P1H who is fixedly connected with housing 0 and one rotatably arranges and with each first planetary pinion of the first internal gear P1H and the first sun gear P1S engagement, first a planetary pinion P1P in these first planetary pinions only is shown in view shown in Figure 1.Each first planetary pinion P1P can be rotated to support on the first row gear rack P1T.
In addition, be provided with the first break B06.In the closed state of this first break B06, the first sun gear P1S is fixing with respect to housing 0.
Each second planetary pinion P2P that the second planetary gear set PGS2 of planetary gear automatic transmission shown in Figure 1 has an internal gear P2H who rotatably arranges, second a sun gear P2S who rotatably arranges and meshes with secondary annulus P2H and the second sun gear P2S, these second planetary pinions can be rotated to support on the second planetary carrier P2T.
As can see from Figure 1, the first sun gear P1S and the second sun gear P2S for good and all rotate and are coupled.Therefore these two sun gears are all the time with an identical rotating speed rotation.
In addition, the planetary gear automatic transmission shown in Fig. 1 also has first clutch K78.In the closed state of this first clutch K78, the first row gear rack P1T and the second planetary carrier P2T rotation are coupled.Therefore in the situation that first clutch K78 closure two planetary carrier P1T, P2T with an identical rotating speed rotation.
As substituting of first clutch K78, also may use the sealed shifting element of a kind of shape, jaw clutch for example is particularly with the jaw clutch of synchronizer.
Also be provided with in addition second clutch K18.In the closed state of this second clutch K18, speed changer input element GE and the second planetary carrier P2T rotation are coupled.
Each third planet gear that third planet gear train PGS3 has the 3rd an internal gear P3H who rotatably arranges, the 3rd a sun gear P3S who rotatably arranges and meshes with the 3rd internal gear P3H and the 3rd sun gear P3S only illustrates a third planet gear P3P in these third planet gears in view shown in Figure 1.Each third planet gear P3P can be rotated to support on third planet gear carrier P3T.
As from can seeing accompanying drawing, the 3rd internal gear P3H and secondary annulus P2H for good and all rotate and are coupled.Third planet gear carrier P3T for good and all is coupled with speed changer drive element GA again.
Be provided with in addition three-clutch K14.In the closed state of this three-clutch K14, the 3rd sun gear P3S and speed changer input element GE rotation are coupled.
Each fourth planet gear P4P that fourth planet gear train PGS4 has the 4th an internal gear P4H who rotatably arranges, the 4th a sun gear P4S who rotatably arranges and meshes with the 4th internal gear P4H and the 4th sun gear P4S, these fourth planet gears can be rotated to support on fourth planet gear carrier P4T.
The 4th internal gear P4H and the 3rd sun gear P3S for good and all rotate and are coupled.
As can see from Figure 1, fourth planet gear carrier P4T and speed changer drive element GA for good and all rotate and are coupled.Can determine in addition, fourth planet gear carrier P4T and third planet gear carrier P3T for good and all rotate and are coupled.
By making second brake B03 closed, the 4th sun gear P4S can be fixing with respect to housing 0.
In addition, the speed changer shown in Fig. 1 also has four clutches K38.In the closed state of this four clutches K38, the second planetary carrier P2T and the 4th sun gear P4S rotation are coupled.
In addition, the feature of the speed changer shown in Fig. 1 also is a kind of hollow shaft structure, and this hollow shaft structure has outer hollow shaft AHW, can be rotatably set in the hollow shaft IHW in it and can be rotatably set in axle W in this boring axle.By described outer hollow shaft AHW, the first sun gear P1S and the second sun gear P2S rotation are coupled.By described boring axle, the rotation of the slave end of the second planetary carrier P2T and second clutch K18 is coupled.By being arranged on the axle in boring axle IHW, the 3rd sun gear P3S is connected with the slave end of three-clutch K14.Three-clutch K14 can be the sealed clutch of a kind of shape, for example jaw clutch especially.
Fig. 2 shows the velocity ratio of each transmission gear.Planetary gear automatic transmission shown in Fig. 1 has nine forward gears and a reverse gear shift altogether.In a kind of specific embodiment, gear speed ratio interval is the speed ratio interval between 1.131(the 5th gear and the 6th gear for example) keep off with 1.692(first and the second speed ratio interval between keeping off) between scope in.The overall ratio interval of speed changer has relatively high value 8.962.
As can see from Figure 2, this speed changer has three so-called " overgear ", i.e. forward gear 7,8,9.
By changing " fixed transmission velocity ratio " (said fixed transmission velocity ratio refers to the ratio of the number of teeth with the number of teeth of sun gear of internal gear) i 0PGS1, i 0PGS2, i 0PGS3, i 0PGS3, can certainly realize other gear stage transition (namely respectively keep off speed ratio interval).
Fig. 3 shows at the gearshift array of the planetary gear automatic transmission shown in Fig. 1 for each gear.The form district of configuration stain represent the shifting element (can realize transmission of torque) of closure.The shifting element (can not realize transmission of torque) that blank form district's representative disconnects.For example, when hanging the 3rd gear, two break B03, B06 disconnect, and clutch K14 is closed, and clutch K18 disconnects, and clutch K38 closure and clutch K78 are closed equally.
In speed changer shown in Figure 1, it is closed that three shifting elements are arranged in each gear all the time and three shifting elements disconnect, this is being useful aspect efficient of speed changer, does not slide or the towing loss because in fact do not produce on the shifting element of closure.

Claims (22)

1. planetary gear automatic transmission particularly has the planetary gear automatic transmission of nine forward gears, wherein is provided with:
-what a speed changer input element (GE) just,
-what a speed changer drive element (GA) just,
-four planetary gear set PGS1-PGS4 just in time, and
-six shifting elements (B03, B06, K14, K18, K38, K78) that be used for to switch each gear of this planetary gear automatic transmission just in time.
2. planetary gear automatic transmission as claimed in claim 1, it is characterized in that, the first planetary gear set (PGS1) is set, each first planetary pinion (P1P) that this first planetary gear set has first internal gear (P1H) that is fixedly connected with the housing (0) of described planetary gear automatic transmission, first sun gear (P1S) that arranges revolvably and meshes with described the first internal gear (P1H) and described the first sun gear (P1S), described each first planetary pinion is bearing on the first row gear rack (P1T) revolvably.
3. planetary gear automatic transmission as claimed in claim 2, is characterized in that, the first break (B06) is set, and in the closed state of this first break (B06), described the first sun gear (P1S) is fixed with respect to described housing (0).
4. planetary gear automatic transmission as described in any one of claims 1 to 3, it is characterized in that, the second planetary gear set (PGS2) is set, each second planetary pinion (P2P) that this second planetary gear set has a secondary annulus (P2H) that arranges revolvably, second sun gear (P2S) that arranges revolvably and meshes with described secondary annulus (P2H) and described the second sun gear (P2S), described each second planetary pinion is bearing on the second planetary carrier (P2T) revolvably.
5. planetary gear automatic transmission as claimed in claim 4, is characterized in that, first and second sun gear (P1S, P2S) for good and all mutually rotates and is coupled.
6. planetary gear automatic transmission as described in claim 4 or 5, it is characterized in that, first clutch (K78) is set, and in the closed state of this first clutch (K78), the first row gear rack (P1T) mutually rotates with the second planetary carrier (P2T) and is coupled.
7. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, second clutch (K18) is set, and in the closed state of this second clutch (K18), described speed changer input element (GE) mutually rotates with the second planetary carrier (P2T) and is coupled.
8. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, third planet gear train (PGS3) is set, each third planet gear (P3P) that this third planet gear train has the 3rd internal gear (P3H) that arranges revolvably, the 3rd sun gear (P3S) that arranges revolvably and meshes with described the 3rd internal gear (P3H) and described the 3rd sun gear (P3S), described each third planet gear is bearing on third planet gear carrier (P3T) revolvably.
9. planetary gear automatic transmission as claimed in claim 8, is characterized in that, described the 3rd internal gear (P3H) for good and all rotates with secondary annulus (P2H) and is coupled.
10. planetary gear automatic transmission as described in any one of claim 8 or 9, is characterized in that, described third planet gear carrier (P3T) for good and all rotates with described speed changer drive element (GA) and is coupled.
11. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, three-clutch (K14) is set, and in the closed state of this three-clutch (K14), the 3rd sun gear (P3S) mutually rotates with described speed changer input element (GE) and is coupled.
12. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, fourth planet gear train (PGS4) is set, each fourth planet gear (P4P) that this fourth planet gear train has the 4th internal gear (P4H) that arranges revolvably, the 4th sun gear (P4S) that arranges revolvably and meshes with described the 4th internal gear (P4H) and described the 4th sun gear (P4S), described each fourth planet gear is bearing on fourth planet gear carrier (P4T) revolvably.
13. planetary gear automatic transmission as claimed in claim 12 is characterized in that, described the 4th internal gear (P4H) for good and all rotates with the 3rd sun gear (P3S) and is coupled.
14. planetary gear automatic transmission as described in any one of claim 12 or 13 is characterized in that, described fourth planet gear carrier (P4T) for good and all rotates with described speed changer drive element (GA) and is coupled.
15. planetary gear automatic transmission as described in any one of claim 12 to 14 is characterized in that, described fourth planet gear carrier (P4T) for good and all rotates with third planet gear carrier (P3T) and is coupled.
16. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, second brake (B03) is set, and in the closed state of this second brake (B03), the 4th sun gear (P4S) is fixed with respect to described housing (0).
17. as the described planetary gear automatic transmission of any one of aforementioned claim, it is characterized in that, four clutches (K38) is set, and in the closed state of this four clutches (K38), the second planetary carrier (P2T) mutually rotates with the 4th sun gear (P4S) and is coupled.
18. the described planetary gear automatic transmission of any one as aforementioned claim is characterized in that, is provided with an outer hollow shaft (AHW), by this outer hollow shaft, the first sun gear (P1S) is coupled with the second sun gear (P2S) rotation.
19. planetary gear automatic transmission as claimed in claim 18, it is characterized in that, be provided with the boring axle (IHW) that arranges in described outer hollow shaft (AHW), by this boring axle, the second planetary carrier (P2T) is connected with the slave end of second clutch (K18).
20. planetary gear automatic transmission as claimed in claim 19 is characterized in that, is provided with the axle (W) that arranges in described boring axle (IHW), by this axle, the 3rd sun gear (P3S) is connected with the slave end of three-clutch (K14).
21. planetary gear automatic transmission as described in any one of claim 11 to 20 is characterized in that, three-clutch is the sealed clutch of a kind of shape, particularly jaw clutch.
22. planetary gear automatic transmission as claimed in claim 6 is characterized in that, the sealed shifting element of a kind of shape is set, this shifting element plays the effect of first clutch (K78).
CN201180045331.1A 2010-11-19 2011-10-20 9 gear planetary gear automatic transmissions Expired - Fee Related CN103154568B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010052001.2A DE102010052001B4 (en) 2010-11-19 2010-11-19 9-speed Planetenradautomatikgetriebe
DE102010052001.2 2010-11-19
PCT/EP2011/005296 WO2012065673A1 (en) 2010-11-19 2011-10-20 9-speed planetary-gear automatic transmission

Publications (2)

Publication Number Publication Date
CN103154568A true CN103154568A (en) 2013-06-12
CN103154568B CN103154568B (en) 2015-11-25

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CN201180045331.1A Expired - Fee Related CN103154568B (en) 2010-11-19 2011-10-20 9 gear planetary gear automatic transmissions

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US (1) US8801563B2 (en)
CN (1) CN103154568B (en)
DE (1) DE102010052001B4 (en)
WO (1) WO2012065673A1 (en)

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US20130252780A1 (en) 2013-09-26
WO2012065673A8 (en) 2013-04-18
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US8801563B2 (en) 2014-08-12
CN103154568B (en) 2015-11-25
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